EP0075252A2 - Automatic twine device for a crop material roll forming machine - Google Patents

Abstract

The binding device comprises a line dispensing device in order to introduce the binding line into the winding chamber of the machine via a line guide arm. A reversible hydraulic drive for pivoting the line guide arm (34) between two positions at each end of the bale can be controlled automatically by a pump drive (27) for the hydraulic pump (38) of the hydraulic drive that can be switched on and off. A control device (29) which responds when a predetermined diameter is reached automatically triggers the switching on of the pump drive (37) and the switching off of the drive at the end of the binding device. A hydraulic control valve (30) is provided between the pump and the hydraulic drive, which is also automatically switched by the control devices (29) depending on the movement of the cord guide arm (34) in order to reverse the drive direction and to switch off the drive at the end of the binding process . A cord cutting device (35) is triggered automatically depending on the movement of the cord guide arm (34) at the end of a binding process in order to cut the cord (33). After the finished bale has been ejected by the driver, the binding device is automatically reset to its initial state depending on the fact that the control device (29) determines that the wrapping chamber is empty. The binding device is now ready for a new binding process. With the aid of a tensioning device (6;) and an open cord guide, the cord guide arm (34) enables the cord end to be inserted quickly and easily into the cord guide arm (34).

Description

The invention relates to an automatic binding device for machines for producing cylindrical bales from crop material in a winding chamber, with a cord dispensing device for inserting a cord into the winding chamber for wrapping the cylindrical bale, which has a cord guide arm, which in an area in front of the winding chamber between end positions and movable, and with a hydraulic drive for cyclically reciprocating the line guide arm, which has a double-acting cylinder, a feed pump, a pump drive for selectively driving the pump and a control valve between the pump and the cylinder, with a valve actuating arm between a first position , in which the cord guide arm is movable from a first to a second position, and a second position is controllable in which the cord guide arm is returned to the first position.

Semi-automatic binding devices for such machines are known (cf. US Pat. Nos. 38 94 484 and 39 13 473). These binding devices have a hydraulically driven cord guide arm which can be moved back and forth before the winding chamber enters. The triggering and termination of the winding process are controlled by hand. The feed Arm speed in the transverse direction in front of the winding chamber is also subject to manual control by setting a flow control valve in the hydraulic drive circuit.

Since such balers are widely used in practice, a number of disadvantages of the binding device have also emerged. First of all, in practice it is desirable that the binding process takes place automatically instead of semi-automatically, in order to relieve the driver. Previously, the driver had to monitor the bale size from his seat on the tractor pulling the machine. When the bale has reached the desired size, the operator must continue wrapping but operate a hydraulic lever to initiate movement of the line guide arm from its one end position on one side of the wrapping chamber. If the string is inserted into the winding chamber together with the crop, the tractor is stopped to interrupt the supply of material to the winding chamber. The lever is held in its adjusted position until the line guide arm has reached the other side and thus the second end position. The line guide arm remains there to make one or more turns around the end of the cylindrical bale. The hydraulic lever is then switched to reverse the hydraulic drive. The result is that the line guide arm is returned to its first position. The speed of the movement of the line guide arm from the second position to its starting position and thus the number of turns of the line around the cylindrical bale is determined by setting the flow control valve in the hydraulic circuit. The flow rate is adjusted so that at least one full turn of the line the end of the bale is laid. The cord is then cut off automatically. With the automation of such a process, the burden on the driver when monitoring the function of the machine that is running behind him is significantly reduced.

Furthermore, it was found that the procedure for threading the cord into the cord guide arm, which in the known case consists of an elongated tubular element which is pivotably mounted at one end, is extremely problematic. You have to push the cord through the elongated tube until the end of the cord reaches the free end of the tube. The cord often gets stuck in the tube and must be manually with the help of a threading link, e.g. of a stiff wire can be drawn into the pipe.

Furthermore, it was found that in the known binding devices, the necessary separating device, which separates the cord at the end of the binding process, must be manufactured with high precision, initially adjusted and maintained accordingly in order to ensure reliable cutting of the cord. In the known separating devices, this is actuated by the movement of the cord guide arm from the second position into the starting position, an abutment being pivoted into engagement with a knife, the cord coming to rest between the two. Any excessive migration of the line guide arm creates an excessive pressure of the abutment on the cutting edge, so that it quickly becomes blunt or even bends.

However, a fully automatic binding device is also known, in which a mechanical drive is connected to the power take-off shaft of the agricultural rattle in order to move two cord guide arms back and forth transversely in front of the winding chamber (cf. US Pat. No. 4,167,844). However, here is the Exceptionally large effort.

It is also known to use a spring drive in a fully automatic binding device in order to move only a single line guide arm from a first side of the machine to the second side, while a hydraulic drive returns the arm to the starting position (see US Pat. No. 4,167) 844). This machine is also complex and cumbersome and prone to failure.

It is an object of the invention to develop an automatic binding device of the type specified in the introduction in such a way that a secure binding process can be carried out automatically with only a single line guide arm, with simple and robust means to be used, a secure wrapping of the bale ends is ensured, the threading the cord in the cord guide arm can be carried out quickly and without additional aids and the cutting device ensures reliable cutting of the cord with a long service life.

This object is achieved in that a control device for triggering a binding process by automatically switching on the pump drive and for moving the valve actuating arm into its first position is provided, which responds to the formation of the cylindrical bale and to the achievement of a predetermined bale diameter, and that The control device automatically switches off the pump drive when the binding process has ended. A simplified, fully automatically operated hydraulic drive for the binding device is obtained in this way. The control is carried out in a simple and safe manner by automatically switching the hydraulic drive on and off, so that the cord into the winding chamber is automatically controlled by a control valve of the hydraulic drive can be initiated.

The control device expediently has a bell lever which can be pivoted depending on the increase in the bale diameter from a first position, which corresponds to the empty wrapping chamber or a wrapping bale of insufficient diameter, into a second position, the second position having a bale diameter corresponding to or exceeding the predetermined value assigned which bell lever triggers the actuation of the pump drive.

The pump drive can consist of a belt drive with a driving and a driven pulley and can have a belt tensioning device. This tensioning device is automatically moved into and out of engagement with the associated belt via the control device, the control device having a linkage for actuating the tensioning device and a tensioning spring which is arranged between the bell lever and the linkage and the tensioning device as a function of the movement of the bell lever biased into a second position in the engaged position.

A locking device locks the boom in the disengaged position. A release element is connected to the bell lever in order to release the locking device when the predetermined bale diameter is reached.

The hydraulic drive expediently has a pinion for swiveling the line guide arm back and forth between its end positions, a clutch device being assigned to the pinion. This makes it possible for the line-guiding arm to linger in its second end position in a predetermined manner, in order to have two or more in the region of the end of the cylindrical bale to lay more than two turns. This arrangement is particularly advantageous in the case of bales which have only a small cylindrical length.

With the new binding device, a line guide arm of great length can be used, which is pivotally supported at one end. The threading of the cord into the cord guide arm is particularly simple and easy to carry out, since the cord guide arm essentially consists of an elongated cord guide surface which is freely accessible from the outside, e.g. is provided on an elongated U-shaped support member. Only a short tubular cord guide is provided at the free end of the cord guide surface, the length of which is considerably less than the length of the cord guide surface. In the area of the line guide surface, the line is held on the surface by a line tensioning device, which maintains the necessary line tension in a simple manner, securely guides the line on the exposed surface and which ensures that the line is easily inserted from the outside.

In a preferred embodiment, the control device has a spring between a valve actuating arm and the bell lever for biasing the actuating arm into its first position when the binding process is triggered and depending on the movement of the bell lever in response to the increase in the bale diameter. The biasing spring of the actuating arm of the control valve biases the actuating arm from its first position also in the direction of the second position, a locking device blocking the actuating arm against movement into the second position being provided, which has an actuating arm which by means of the cord guide arm during its movement from the first into the second position for releasing the locking device and for releasing the actuating arm for movement into its second position. So if the Cord guide arm reaches the second position on the other side of the winding chamber, the locking device is released and the actuating arm for the control valve is moved into its second position under the action of the associated pretensioning device, as a result of which the hydraulic drive is switched over so that the cord guide arm is moved from the second position is returned to the first or starting position.

The return spring is advantageously designed and arranged such that it also biases the actuating arm into a third position, the control device being designed so that the actuating arm is automatically moved from the third to the first position by the biasing spring when a binding process is triggered should. In the third position, the hydraulic drive is disabled. The actuating arm occupies the third position at the end of a binding process. The pivoting of the actuating arm into the third position takes place with the effect of pivoting the arm in a direction generally opposite to the direction which is necessary when the arm is initially displaced from the third to the first position and from the first position to the second position. This makes it possible to use a two-position valve as the control valve, but to give the associated actuating arm three different positions, namely a rest position and a first position for the drive in one direction and a second position for the drive in the opposite direction. The valve remains in its second position when the associated actuating arm is moved from the second to the third position. Thus, when the operating arm is moved from the third to the first position, the valve is switched from the second to the first position and switched back when the operating arm is pivoted from the first to the second position.

The coupling mentioned in the drive connection for the line guide arm expediently comprises two tooth members with tooth-free sections for interrupting the engagement, so that one tooth member can continue to be driven without transmitting the driving force to the first tooth member and the line guide arm. Energy can be stored by means of a corresponding pretensioning device when the line guide arm reaches a side wall of the winding chamber, where the arm remains to lay several turns, this energy being released in order to subsequently bring the teeth of the two tooth members back into engagement again. This gives the bale a high degree of shape retention in the area of its ends.

To control the cutting device, a control arm is provided, which is also movable in three positions. In the first position, the cutting blade is out of engagement with the abutment over which the cord to be cut runs. In the second position of the control arm, the knife is in engagement with the abutment for the purpose of severing the cord. In the third position, the knife is still in engagement with the abutment. This means that when the control arm is pivoted between the second and third positions, the knife remains at rest. This means that the control arm actuated by the cord guide arm for the cutting device can continue its movement after the separating cut has been carried out without the knife being excessively loaded. As a result, the cutting device maintains a significantly longer service life. In addition, the cut can be carried out much more precisely and the corresponding cutting elements can be adjusted more precisely against one another.

The invention is explained in more detail below with the aid of schematic drawings using several exemplary embodiments.

• Figur 1 eine Seitenansicht von der rechten Seite einer Maschine größerer Abmessungen zur Herstellung von zylindrischen Ballen mit einer automatischen Bindeeinrichtung gemäß der Erfindung.
• Figur 2 eine seitliche Querschnittsdarstellung der Wickelkammer mit Einlaß nach Fig. 1, wobei der Schnurführungsarm in einer Stellung gezeigt ist, in der er die Schnur in die Wickelkammer einleitet.
• Figur 3 einen Querschnitt entlang der Schnittlinie III-III der Figur 1, wobei ein Abschnitt der Steuereinrichtung gezeigt ist.
• Figur 4 eine Seitenansicht eines anderen Bereiches der Steuereinrichtung für die automatisch arbeitende Bindeeinrichtung in der bevorzugten Ausführungsform nach Fig. 1.
• Figur 5 in perspektivischer Darstellung den gleichen Bereich der Steuereinrichtung nach Fig. 4, wobei in Fig. 5 die hydraulische Pumpe nach Fig. 4 nicht dargestellt ist.
• Figur 6 eine Draufsicht auf eine Ausführungsform einer Schnurabgabeeinrichtung der Bindeeinrichtung nach der Erfindung, wobei die Vorrichtung in Blickrichtung von vorne nach hinten dargestellt ist.
• Figur 7 eine vordere Ansicht der Schnurabgabeeinrichtung nach Fig. 6.
• Figur 8 eine Draufsicht auf ein zweites Ausführungsbeispiel einer Schnurabgabeeinrichtung für die automatische Bindeeinrichtung nach der Erfindung, wobei die Abgabeeinrichtung in Blickrichtung von vorne nach hinten wiedergegeben ist.
• Figur 8a im Ausschnitt und Draufsicht die Vorrichtung nach Fig. 8 ergänzt durch eine Kupplungseinrichtung, wobei das Getriebe in einer Stellung gezeigt ist, in der der Schnurführungsarm auf einer Seite der Wickelkammer für einen Moment verharren kann.
• Figur 9 eine Vorderansicht der Abgabeeinrichtung nach Figur 8.
• Figur 10 im Ausschnitt einen Querschnitt der Abgabeeinrichtung nach Fig. 8.
• Figur 11 eine allgemein schematische Darstellung der Bindeeinrichtung mit Einzelheiten des schematisch wiedergegebenen hydraulischen Schaltkreises.
• Figur 12 eine perspektivische Ansicht der Schneideinrichtung der automatisch arbeitenden Bindeeinrichtung nach der Erfindung.
• Figur 13 im Ausschnitt eine Seitenansicht des Messers der Schnurschneideinrichtung nach Fig. 12.
• Figur 14 in größerem Querschnitt eine Schnurspanneinrichtung nach Fig. 7, wobei der Schnitt entlang der Schnittlinie XIV-XIV geführt ist und
• Figur 15 eine vergrößerte Darstellung der Spanneinrichtung nach den Figuren 6 und 7.

Show it:

• Figure 1 is a side view from the right side of a machine of larger dimensions for the production of cylindrical bales with an automatic binding device according to the invention.
• Figure 2 is a side cross-sectional view of the winding chamber with inlet according to Fig. 1, the cord guide arm being shown in a position in which it introduces the cord into the winding chamber.
• 3 shows a cross section along the section line III-III of FIG. 1, a section of the control device being shown.
• FIG. 4 shows a side view of another area of the control device for the automatically operating binding device in the preferred embodiment according to FIG. 1.
• 5 shows a perspective view of the same area of the control device according to FIG. 4, the hydraulic pump according to FIG. 4 not being shown in FIG. 5.
• Figure 6 is a plan view of an embodiment of a cord delivery device of the binding device according to the invention, the device being shown from the front to the rear in the viewing direction.
• FIG. 7 shows a front view of the line dispenser according to FIG. 6.
• FIG. 8 shows a plan view of a second exemplary embodiment of a line dispensing device for the automatic binding device according to the invention, wherein the dispenser is shown from the front to the rear in the viewing direction.
• Figure 8a in detail and plan view of the device of Fig. 8 supplemented by a coupling device, the transmission being shown in a position in which the cord guide arm can remain on one side of the winding chamber for a moment.
• FIG. 9 shows a front view of the dispensing device according to FIG. 8.
• 10 shows a detail of a cross section of the dispensing device according to FIG. 8.
• Figure 11 is a generally schematic representation of the binding device with details of the schematically represented hydraulic circuit.
• Figure 12 is a perspective view of the cutting device of the automatic binding device according to the invention.
• FIG. 13 shows a detail of a side view of the knife of the line cutting device according to FIG. 12.
• 14 shows a larger cross section of a cord tensioning device according to FIG. 7, the cut being made along the section line XIV-XIV and
• FIG. 15 shows an enlarged illustration of the tensioning device according to FIGS. 6 and 7.

1 and 2 show a machine 11 for producing cylindrical bales of large dimensions. The device has an automatic binding device 12, which is designed according to a preferred exemplary embodiment of the invention. FIG. 1 is a simplified side view of the machine 11 which is suitable for producing cylindrical bales from hay or other material. Figure 2 is a cross-sectional view in detail from the front of the machine 11. The machine 11 comprises two wheels 13, only one of which is shown, so that the machine is pulled by a tractor, not shown, over the attachment with the aid of the tension member 15 over the field can be. The machine is driven by connection to a conventional PTO gearbox on the rear of the tractor. The machine 11 further comprises two upright and opposite side walls 17, 18 extending in the direction of travel, which are stiffened by cross members, not shown. A winding chamber 22 is delimited between the side walls 17 and 18 by a plurality of belts 14 supported by a plurality of transverse rollers 20, only a few of which are shown in FIG. 2. The arrangement and storage of the rollers and guiding of the belts is not part of the present invention. A detailed description is therefore unnecessary.

The machine has a mechanism 19 of conventional design which receives the crop, which is mounted below the side walls 17 and 18 in such a way that it introduces the crop picked up from the ground into the winding chamber 22. When the material is introduced into the wrapping chamber 22 and the bale increases in diameter as a result, the size of the wrapping chamber and the density of the bale formed therein are controlled by a chuck 21 which is also not the subject of the present invention. The instep device 21 therefore only needs to be briefly described. It comprises two control arms 23, only one of which is shown, which are each mounted on the outside of the side walls 17 and 18. The necessary tension is generated by two hydraulic cylinders 25 (only one of which is shown) and by two spring arrangements 27. When the resulting bale 24 increases in diameter, the arm 23 in FIG. 1 is pivoted counterclockwise against the tension generated by the cylinders 25 and the spring arrangement 27. When the bale formation in the wrapping chamber is complete or the bale reaches a predetermined diameter, a binding process is initiated, and the wrapping device 12 is actuated to wrap a wrapping cord around the circumference of the bale 24.

As shown schematically in FIG. 11, the binding device 12 comprises a cord dispenser or feed device 30, which is shown in more detail in FIGS. 2, 6 and 7, and which serves to guide the cord 33 into the winding chamber 22. Furthermore, the device comprises a hydraulic drive 32, which is shown in FIG. 11 in the form of a circuit diagram, in order to cyclically move a line guide arm 34 of the line output device 30 shown in FIGS. 2 and 5 to 7 in front of the winding chamber 22.

Furthermore, a control device 29 is provided, which is shown in more detail in FIGS. 3 to 5, in order to trigger a wrapping process by sensing the increase in the diameter of the bale 24, in order to automatically generate a pump drive 37 for driving a hydraulic pump 38 at a predetermined diameter 4 and is omitted in FIG. 5, and in order to bring a two-position control valve 39 into a first position and, on the other hand, to end the winding process in that the hydraulic drive 32 after the winding has been wrapped around the Turn off bale 24 with the cord 33. After the winding process has ended, the cord 33 is automatically cut by a cord separating device 35 according to FIGS. 12 and 13. After severing the cord 33, the driver actuates an ejection device, not shown, which actuates a hydraulic cylinder 44 according to FIG. 1 in order to open the wrapping chamber 22 and to allow a bale to roll out onto the ground. After the bale has been ejected, the machine 11 is then ready to start the formation of another bale.

The control device 29 for the automatic binding device is described in more detail with reference to FIGS. 1 and 3 to 5. The control device 29 comprises a member 40 which senses the bale diameter and is arranged between a control arm 23 and a bell lever 41. The sensing member 40 is slidably mounted to energize the control arm 23. For this purpose, the link 40 is guided through a sleeve 42 which is pivotally articulated on the arm 23 at 43. The effective length of the link 40 can be adjusted by arranging a split pin 45 in one of several bores 47 at one end of the link 40. The position of the split pin 45 determines the size of the empty movement, which is provided in the movement sequence of the control arm 23 during bale formation, before the sleeve 42 engages the split pin 45 in order to move the link 40 upward to the right in FIG. 1 and to initiate the binding process. The shorter the effective length of the link 40, the smaller the diameter of the bale until the binding process is triggered. The link 40 is screwed at one end to the bell lever 41, so that the. Bell lever 41 moves clockwise from position D, which corresponds to the empty wrapping chamber or a bale whose diameter is smaller than the predetermined value, to position E, which corresponds to a completed bale in the winding chamber 22 corresponds. Here, the link is moved to the top right in Fig. 1 to initiate the binding process.

According to a further aspect of the new embodiment of the binding device, the bell lever 41 is moved into the position E according to FIG. 4, so as to trigger the drive of the pump 38 of the hydraulic drive 32 by actuating the pump drive 37. An arm 49 of the bell lever 41 is connected to a End of a spring 53 connected to a belt tensioner. The other end of the spring 53 is connected to the tensioning device 65 of the pump drive 37 via a linkage 54, the tensioning device being movable between a position engaging the belt and a disengaged position. The linkage 54 is formed by an angle or bell lever 59, a flange 55 which is fastened to the second end of the spring 53 and to a first arm 57 of the bell lever 59 and a link 63 which forms the second arm 61 of the bell lever 59 the tensioning device 65 connects. The latter includes an idle wheel or pulley 66 which is freely rotatably mounted on an arm 67 which is pivotally mounted at 69.

The pump drive 37 further comprises a driving pulley 71 which is connected in a manner not shown to the PTO of the agricultural tractor and a driven pulley 73 which is connected to the driving pulley 71 via a belt 75.

The engagement of the pump drive 37 is controlled precisely by triggering only at the moment when the bale 24 reaches a predetermined diameter. The release takes place with the aid of a pawl 77, which fixes the bell lever 59 in its first position, which corresponds to the empty wrapping chamber or a bale of too small a diameter. The pawl 77 is actuated by the engagement of a tongue 79, the second Arm 49 of the bell lever 41 is connected by a link 81. The pawl 77 is pivotally mounted at 83 and biased into the locking position by a return spring 86. When the bell lever 51 is pivoted clockwise to position E depending on the formation of a bale in the wrapping chamber to a predetermined diameter, the spring 53 is tensioned and at the same time the link 81 and the tongue '(9 backwards, ie 4 to the left in Fig. 4. With this backward movement of the tongue 79, an arm 35 of the pawl 77 finally engages with the tongue 79, so that the pawl 77 pivots counterclockwise about the pivot point 83 and thus releases the bell lever 59, so that this pivots counterclockwise under the action of the tension spring 53. With the pivoting of the bell lever 59 counterclockwise, the tensioning device 65 is pivoted into engagement with the belt 75, the tension of which establishes the drive connection between the pulleys 71 and 73.

At the end of a binding process, a return spring 84, which is provided between a frame member 86 and the flange 55, ensures that the linkage 54 is moved into the disengaged position of the tensioning device when there is no counter-tension by the spring 53. The linkage 54 is then locked again in this position by the pawl 77.

The control device 29 according to FIG. 4 is further designed such that it monitors the actuation of a hydraulic two-position control valve 39. For this purpose, a valve actuation arm 89 is pivoted between three valve control positions. A position, namely position A is a rest position. The actuating arm 89 accepts this in the time between two binding processes. Position B serves to move the cord guide arm 34 from the left to the right of the machine. Position C is used for the line guide arm 34 to move from the right back to the left. When the actuating arm 89 is in positions A and C, the two-position control valve 39 assumes the position shown in FIG. 11. When the actuating arm 89 is in position C, the valve 39 assumes its second position, not shown in FIG. 11, in which the lower control region of the slide is effectively switched into the hydraulic circuit according to FIG. 11. Referring to Fig. 5, it can be seen that the control device 29 has a spring 91 for the actuating arm, which is arranged between the tongue 79 and the actuating arm 89 and the arm 89 in the positions B and C depending on the completion of a bale in biases the winding chamber 22. A return spring 93 for the actuating arm is attached to the arm 89 to bias it into position A at the end of a binding operation when the biasing spring 91 is released. When a bale of a predetermined diameter is formed in the wrapping chamber 22 and the bell lever 41 is pivoted counterclockwise, sufficient tension is applied by the spring 91 to the actuator arm 89 to overcome the resistance of the spring 93 and the arm 89 out of position A. to move to position B. In this position, the hydraulic drive 32 moves the line guide arm 34 from the left side to the right side of the machine. The actuator arm 89 cannot move from position B to position C because of the pawl 95. The pawl 95 includes a latch 99 with a finger 97 at one end which cooperates with the underside of the actuator arm 89. An actuating arm 101 for the pawl is connected to the locking member 99 via a member 103. When the actuating arm 89 is moved from the position A to the position B, a pin 92, which is articulated at one end to a lower plate 94 of the actuating arm 89 and engages with the other end on the slide of the valve 39, ge pulled so that one end of the plate 94 engages the top of the finger 97 and the other end comes into contact with the bottom of a stop 106. The finger 97 is pivotally mounted in the side wall 17 and can be rotated counter-clockwise against the action of the spring 105 depending on the mutual action of the arm 101 and the line guide arm 34 at the end of the movement from the left side to the right side of the machine. When the locking member 99 is rotated clockwise, the spring 91 pivots the actuating arm 89 into position C. The result is that the cord guide arm 34 is guided from the right side to the left side of the machine. When moving from position B to position C, plate 94 is pivoted counterclockwise and downward so as to push pin 92 inward.

In operation, crop is introduced into the winding chamber 22 and a bale 24 of increasing diameter is wrapped. The size of the winding chamber 22 is monitored by the control arm 23 which is pivoted in the clockwise direction in FIG. 1. When the bale 24 is nearing its completion, the sleeve 42 according to FIG. 3 will act on the control arm 23 on the cotter pin 45 at the end of the sensing element 40. The sensing element is then moved upwards with the control arm 23. 4 and 5, the bell lever 41 is pivoted clockwise from position D to position E. As a result, the tensioning spring 53 and the spring 91 for the actuating arm begin to stretch. When the bell lever 41 reaches position D, the tongue 79 engages and pivots the arm 45 of the pawl 77 such that the bell lever 59 is released. As a result, the tension of the spring 53 acts on the connecting rod 54 so that it moves the tensioning device 65 into the engaged position against the action of the return spring 84.

The pump drive 37 is thus activated and the pump 38 is started in order to start the hydraulic drive 32 for the line output device 30. When the spring 91 for the actuating arm is tensioned from the position D into the position E by the movement of the bell lever 41, sufficient tension is applied to the actuating arm 89 to overcome the counterforce of the return spring 93 on the actuating arm 89. This is therefore pivoted from position A to position B in Fig. 4. The actuating arm 89 assumes position B before the tongue 79 disengages the pawl 77 for engaging the pump drive 37. When moving from position A to position B, the actuating arm pivots counterclockwise and upward with respect to pin 92. This is thus pulled up to cause hydraulic drive 32 to cause cord guide arm 34 from the left near the wall 18 to move to the right side near the wall 17. When the cord guide arm 34 reaches the right side and engages the actuator arm 101 of FIGS. 5 and 6 to release the pawl 95, the actuator arm 89 of FIG. 1 is moved from the B position to the C position, again by the Effect of the spring 91.

This movement causes the pin 92 of the valve 39 to move inward to reverse the hydraulic actuator 32. Thus, the line guide arm 34 is moved from the right side to the left side. At the end of this path, the line guide arm 34 engages the line separation device 35 according to FIGS. 6 and 12, which is activated to cut the line 33. The driver or another operator then operates a conventional device, not shown, which uses the cylinder 37 to ensure that the bale 24 is ejected from the wrapping chamber 22. After the ejection, the control arm 23 is pivoted counterclockwise, with the sensing element down is moved. The bell lever 41 from position E to position D under the action of springs 53, 84, 91 and 93. The return spring 34 resets the linkage 54 so that the tensioning device 65 disengages from the belt and the pump drive 37 is switched off becomes. The bell lever 59 can thus be locked in the disengaged position by the pawl 77.

When the bell lever 41 is moved from the E position to the D position, the tension of the spring 91 is reduced and reaches a size so that the return spring 93 can pivot the actuating arm 89 from its C position back to the A position. The position of the valve 39 remains unchanged during this movement. With the switching off of the pump drive 53 and the return of the actuating arm 89 from position C to position A, the binding process is thus ended. The machine is thus conditioned in such a way that a further binding process can subsequently be triggered when a new bale in the wrapping chamber reaches the corresponding diameter.

The line feed device 30 is explained in more detail below with reference to FIGS. 6, 7, 14 and 15.

The cord feed device 30 comprises a cord guide arm 34. This has a tubular guide 107 for receiving a cord, a U-shaped support part 109, a cord tensioning device 114 and a conventional cord supply (not shown) for feeding the cord 33 to the cord guide arm 34.

The support member 109 has an elongated exposed guide surface 116 along which the cord is guided from its cord source before the cord enters the tubular guide 107. The guide 107 is much shorter than the support part 109, so that the threading of the Cord is significantly simplified. For this purpose, the cord only needs to be guided along the exposed surface 116 of the supporting part and threaded through the tensioning device 114 and inserted into the tubular guide 107. Since the latter is short, for example only 16 cm, threading is extremely simple and can be carried out by hand without the aid of mechanical devices, while known long pipe guides require mechanical threading devices such as wires or the like.

The cord tensioning device 114 is a simple device for arranging the cord 33 on the guide surface 116. It also supplies sufficient tension in the cord 33 to prevent tangling and unnecessary pulling of the cord from the cord supply. The clamping device 114 comprises a plate 118 and a mounting device 122. This comprises a bolt 124 and a spring 126 mounted coaxially thereon, with the aid of which the plate 118 is pivotably mounted on the support part 109. The plate 118 is biased against the surface 116 by the spring. Two guide pins 128 and 130 are each arranged adjacent to the inlet 136 and the cord outlet 138 of the plate 118 on the support part 109. Together with the bolt 124, they form a guideway for the cord through the tensioning device. This simultaneously holds the cord on the elongated guide surface 116. The entry side 136 has a bevelled edge 139. This allows easy free movement of the cord 33 through the tensioning device 114. The distance between the pins 128 and 130 is approximately equal to the width of the plate 118 plus the diameter of the cord 33, so that the cord 33 between input 136 and output 138 and the Pins 128, 130 can be threaded through, one after the other. An upper surface 140 extends between entrance 136 and exit 138 and has an ab bevel 142 provided, which allows easy insertion of the cord 33 under the plate 118. The exit edge 138 is not beveled and lies in the plane of the plate 118, so that the edge engages the cord 33 and resists the accidental pulling of the cord 33.

The line guide arm 34 is in front of the winding chamber between a first position at approximately minus 15 ° (here as a solid line on the left side of the machine according to FIG. 6) and a second position of approximately plus 195 ° (here dashed in FIG. 6 reproduced) moved back and forth. The line guide arm 34 is moved between these two end positions with the aid of a hydraulic cylinder 112 of the hydraulic drive 32 according to FIG. 11. The cord guide arm 34 is fastened to a toothed member 110 which is rotatably mounted in the support part 109. The cylinder 112 is in driving engagement with the gear 110 via a link 103 which is pivotally articulated to one end of the piston 108 of the cylinder 117 and is attached to a second gear 117 with the other end. The second toothed member 117 is pivotally mounted in a support part 111 for the line guide arm centrally between the side walls 17 and 18 and is in direct tooth engagement with the toothed member 110.

Cord guides 113 and 114 are attached to the side walls 18 and 17, respectively, to limit the path of the cord 33 into the winding chamber 22. The cord 33 cannot come closer to the side walls 18 and 17 by engaging the cord guides 113, 115 than is determined by the position of the vertical legs of the guides 113, 115. The result is that the additional turns of the cord around each end of the bale formed in the wrapping chamber are given a predetermined position at the end of the cylindrical bale. These additional turns are created on the bale due to the fact thing that the cord guide arm 34 is swung substantially beyond the point in question at which the cord is held back by the cord guides 113, 115, whereby by this swinging out the cord guide arm reaches its first and second end positions at approximately minus 15 ° and plus 195 ° .

In operation, the line guide arm is initially on the left near the side wall 18. In this position, the tying process is initiated. It is triggered by the control device 29, which responds to the completion of the bale formation and controls the valve 39 into a position in which the drive 37 for the pump is started and the piston 108 is extended. For this purpose, the pump 38 supplies fluid to the cylinder 112 so that the piston 108 extends. When the piston 108 extends to the side wall 18 in FIG. 6, the line guide arm 34 is pivoted from the first position to the second position on the right side. When the cord guide arm 34 has reached a position in the middle between the side walls 17, 18, the end of the cord 33 between the straps and the bale is grasped and drawn into the winding chamber with the incoming crop. The actual binding process begins. The cord 33 is first wound from a point in the middle of the bale to the right side of the bale. Additional turns are made at the end of the bale by placing the line 33 against the guide 115, while the line guide arm 34 continues to move until it contacts the pawl 95. The line guide arm 34 bears against the actuating arm 101 to disengage the pawl 95 when the piston 108 is fully extended. When the pawl 95 is disengaged, the actuating arm 89 for the valve moves from the B position to the C position, under the action of the spring 91. The valve 39 is switched over so that the hydraulic cylinder 112 is subsequently reversed in its drive , whereby the line guide arm 34 is returned from the second position back to the first or starting position. Here, the cord 33 is continuously drawn into the winding chamber 22. When the piston 108 is fully retracted, the line guide arm 34 rests on the actuating part of the line separating device 35 in order to cut the line 33.

When the cord tensioning device 114 is in operation, the cord 33 is first threaded through the tensioning device 114. For this purpose, a cord section is first inserted between the bevelled edge 142 and the guide surface 116. Thereafter, the cord portion near the input side 136 of the plate 118 is pulled out and down, causing the plate 118 to pivot clockwise. This allows the cord to slide between the input 136 and the pin 128 and lies between the pin 128 and the pin 124. Then the cord segment near the output 138 is pulled out and down to pivot the plate 118 counterclockwise. The cord thus slides between the edge 138 and the guide pin 130 and thus lies between the latter and the bolt 124. The threading of the cord into the cord guide arm is completed by pushing the cord end through the short guide tube 107.

From the foregoing description, it can be seen that threading the cord into the cord guide arm 34 can be accomplished quickly and easily without the operator having to perform a difficult task since all parts are easily accessible.

It is expressly pointed out here that the clamping device 114 shown and described has a practical significance and corresponding advantages which go beyond the application in the machine for producing cylindrical bales. For example, the Tensioning device 114 can also be used in a binding device for other types of balers, namely wherever it is necessary to feed the cord in one direction under tension.

An alternative embodiment of a cord dispenser is shown at 120 in FIGS. 8-10. In this embodiment, the advantage is that it can be used especially in machines of small width and thus short bale length, in which it is desirable to use a relatively longer cord guide arm 36 compared to the use of the cord guide arm 34 in the embodiment of FIG Cord delivery device 30. This is particularly suitable for longer bales. The cord guide arm 36 can be of the same length as the cord guide arm 34, but its length is relatively greater in relation to the length of the bale.

The line guide arm 36 is in front of the winding chamber 22 between a first or rest position, as shown in full lines on the left side of the machine and corresponds to a position of minus 30 °, in a second position, which is shown in broken lines (of about 100 ° ) moved back and forth with the aid of a hydraulic drive 32 according to FIG. 11. In addition to the line guide arm 36, the line dispenser 120 includes a conventional line supply, not shown, and a gear 127 that provides drive engagement between the hydraulic drive 32 and the line guide arm 36. The cord guide arm 36 has a tubular guide 123 of short length, a supporting part 125 which is connected at one end to the guide 123 and the other end is connected to the gear 127, and a cord tensioning device 144. The design and mode of operation of the tensioning device 144 is identical to that of the tensioning device 114 further explanation is therefore not necessary in the present context. The gear 127 comprises a first toothed member 129 which is rotatably mounted on the support part 131 to the right of the center line between the side walls 17, 18 and which has teeth 133 over a circumferential section. This toothed member is firmly connected to the cord guide arm 36. The transmission has a second toothed member 134 which is rotatably mounted on the supporting part 131 and has teeth 135 on a circumferential section which are in direct engagement with the teeth 133 of the toothed member 129. The transmission 127 is driven by the hydraulic cylinder 112 of the drive 32 with the aid of the second gear 134, the piston 108 of the cylinder 112 being fixedly connected to the tooth member 134 via the connecting member 137. The transmission 127 comprises a coupling device 141. This allows the cord guide arm 36 to remain near the side wall 17 in the second position. The dwelling effect means that additional turns can be placed around the end of the bale. The coupling device 141 comprises a surface element on at least one of the circumferential surfaces of the first toothed member 129 and the second toothed member 134 in order to interrupt the drive engagement between these two and to enable the second toothed member 134 to continue to be driven without the first toothed member 129 and the associated member Cord guide arm 36 are moved. The surface elements are formed here by a smooth or toothless surface 143 on the circumference of the tooth member 134 and by a rear toothless surface on the tooth member 129. As FIG. 8a shows, when the line guide arm 36 reaches the second position near the side wall 17, the tooth-free surface 143 contacts the back of the tooth member, thereby interrupting the driving engagement between the tooth members 134, 129. In order to ensure renewed engagement when the clutch device 141 is engaged by renewed engagement of the teeth 133 with the teeth 135, a pre-tensioning device 147 is provided. This includes a lever 149 which is fixedly attached to the tooth member 129. Furthermore, a spring 151 is attached to the frame of the machine. The spring 151 includes a piston 153 that is biased by a spring 156 to extend upward to the right in FIG. 8. The spring 156 surrounds the rod 153 and lies between a support member 155 and a stop 157 which is fixedly attached to the rod or the piston 153. When the line guide arm 36 is in the second position near the side wall 17, the lever 149 engages the piston or rod 153. This compresses the spring 156 to store a sufficient amount of energy therein. This ensures that the teeth 133 of the tooth member 129 engage the teeth 135 of the tooth member 134 again when the hydraulic drive 32 is reversed to return the line guide arm 36 back to its original position near the side wall 18.

The reversal of the hydraulic drive 32 is achieved in a similar manner to that described in the exemplary embodiment according to FIGS. 5 to 7, with the exception of the special design of the locking device 159 for the valve. This comprises a locking member 161 with a finger 162 which engages on the underside of the valve actuating arm 89 when it is in the B position. Counterclockwise rotation of the latch member 161 allows the actuator arm 89 to be moved from position B to position C to reverse hydraulic drive 32 and the cord guide arm 36 from the second position near sidewall 17 to its initial position attributed to the side wall 18. A counterclockwise rotation of the locking member 161 is brought about by a movement of the cord guide arm 36 into the second position. The connecting member 137 engages an actuating arm 163, which is connected to the locking member 161 via the bell lever 165, which is rotatable on the side wall 17 at 167 is mounted, and by a link 169 which is articulated at one end to the bell lever 165 and at the other end to the locking plate 171. The locking member 161 is articulated on the locking plate 171. The movement of the actuating arm 163 to the left in FIG. 8 as a function of an adjustment of the link 137 by the extension of the piston 108 of the hydraulic cylinder 112 leads to a rotation of the bell lever 165 in a clockwise direction about the pivot point 167. This rotation of the bell lever according to FIG. 8 results in a counterclockwise rotation of the locking member 161 in FIG. 10, namely via the connecting member 169 and the locking plate 171. The result is a reversal of the hydraulic drive 32, as previously described in connection with the retraction of the piston 108. The actuator arm 183 is then moved to the right in FIG. 8 as a result of the link 137 becoming disengaged by the action of the return spring 173 which biases the bell lever 165 counterclockwise in FIG. 8, while the latch member 161 in the clockwise direction in FIG. 10 is biased and adjusted.

A cord guide 174 is provided on the left side wall 18 to terminate the movement of the cord 33 while the cord guide arm 36 completes its lateral stroke to the first or rest position. This leads to the application of additional wraps around the cord at the left end of the bale 24.

In operation, when the bale has reached a predetermined diameter, the control device moves the actuating arm 89 from position A to position B to activate the hydraulic drive 32 and thus cause the piston 108 of the cylinder 112 to extend. The actuating arm 89 is in position B due to the engagement of the locking member 161 and Stop 106 held. When the piston 108 is extended, the link is rotated clockwise to cause the second tooth member 134 of the transmission 127 to rotate clockwise. The clockwise rotation of the tooth member 134 leads to a counterclockwise rotation of the first tooth member 129. In this way, the cord guide arm 36 is pivoted clockwise until the coupling device 141 disengages by engaging the tooth-free surface 143 on the rear side of the tooth member 129 As a result, the line guide arm 36 is held in the second position near the side wall 17 while the tooth member 134 continues to rotate. The rest leads to additional loops of the cord being placed around the right end of the bale 24. At the end of the stroke of the piston 108, the connecting member 137 rests on the actuating arm 163 of the locking device 159 in order to reverse the hydraulic drive 32. The actuator arm 163 is shifted to the left in FIG. 8 to cause the bell lever 165 to rotate clockwise, which causes the latch member 161 to rotate counterclockwise. When the locking member 161 is rotated in this way, the actuating arm 89 of the valve is moved from the B position to the C position under the action of the spring 91. With the actuating arm 89 in the C position, the hydraulic drive 32 is reversed around the line guide arm 36 from the second position of the side wall 1 '(to move to its starting position near the side wall 18.

Simultaneously with the pivoting of the actuating arm 163 to the left in FIG. 8, the lever 149 of the toothed member 129 will compress the spring 156 of the spring device 151 in order to store sufficient energy for the pretensioning of the lever 159 in the clockwise direction, so that the teeth 133 and 135 re-engage is ensured. When the switching of the hydraulic drive 32 has been carried out by the valve 87, the Piston 108 retracted, line guide arm 36 pivoted until the piston is fully retracted and arm 36 has returned to its first home position near side wall 18. In this position, the cord cutting device 35 is operated to cut the cord 33, as will be explained further below. From this point on, the end of the wrapping or binding process takes place identically, as described above in the exemplary embodiment according to FIGS. 6 and 7.

An advantage of the embodiment of the cord dispenser 120 according to FIGS. 8 to 10 is better understood if one compares this embodiment with the embodiment 30 according to FIGS. 6 and 7. The following features are preferred for the formation of the line guide arm: In connection with space limitation, the line guide arm must be arranged essentially in front of the winding chamber 22. In addition, the arm must be long enough to be transferred from the first position to a position where the beginning of the line is so close to the winding chamber that the beginning of the line with the crop can be drawn into the winding chamber. Third, additional turns must be wound up at the ends of the bale. In the embodiment according to FIGS. 6 and 7, the line guide arm 34 is short enough to allow it to continue to travel beyond the zero degree position and the 180 position. This means that the arm 34 in FIG. 6 is swung over a floor of approximately minus 15 ° to plus 195 °, additional wraps being effected with the aid of the guides 113, 115. These features are realized for machines with a working width of 156.10 cm (based on the winding bobbin) and a length of 73.4 cm for the line guide arm. However, these features are difficult to achieve when dealing with bales of shorter length, for example with a working width of 117 cm. In the embodiment according to FIGS. 8 to 10 these features are obtained with a cord guide arm 36, which can have the same length, ie 73.4 cm, as the arm 34 of the exemplary embodiment according to FIGS. 6 and 7. The cord guide arm can also be pivoted substantially in front of the winding chamber and has one sufficient length to bring the cord 33 close to the inlet of the winding chamber so that the cord end can be taken up by the incoming material. By shifting the pivot axis of the cord guide arm to the right with respect to the point between the side walls 17 and 18, this cord guide arm can also be pivoted between a zero degree position and an angle of minus 15 °. It is therefore suitable for making additional turns in connection with the guide 174 at least around the left end of the bale in the wrapping chamber. To the right side of the twine 36 but only up to an angle of about 113 ⁰ pivotable. Here, the additional turns required are achieved by stopping the line guide arm 36 for a while, by the coupling device 141 interrupting the drive engagement of the transmission 127. The essential features are thus also realized in a machine with a small working width according to FIGS. 8 and 10.

The cord separation device 35 is described in more detail below with reference to FIGS. 12 and 13.

The cord separating device 35 can be used with both embodiments according to FIGS. 6 and 7 and 8 to 10. The 3-cord separating device 35 is explained in more detail below in connection with the first exemplary embodiment (FIGS. 6 and 7). The cord separating device 35 comprises an abutment 175, an angular or bell-shaped knife 177 which is mounted on a shaft 179 and can be pivoted between a position engaging on the abutment and a position removed from the abutment as shown in FIG. 13, and an actuating device 181, to pivot the knife 177 between the two positions depending on the movement of the line guide arm 34. The actuator 181 includes an extendable guide 183 and a control arm 185. One end of this control arm is slidable in a holder 186. The other end is slidably supported between slotted fingers 197, 189. The whole is the extendable guide 183.

A spring biasing device 191 biases the actuator 181 and the extendable guide 183 toward the rear end of the machine so that the knife 171 assumes its position away from the abutment, as shown in phantom in FIG. 13. The pretensioning device 171 comprises a spring which surrounds the control arm 185 and is arranged between the holder 186 and a stop, which is designed here as a washer 193 and as a pin 201.

A biasing member 199 serves to bias the control arm 185 into the retracted position of the slotted fingers 197, 189, namely towards the rear of the machine. The biasing member 199 is designed here as a coil spring that surrounds the control arm 185 and between a stop plate 201 on one End of the extendable guide 185 and a stop washer with pin 203 is arranged. The spring device 191 is dimensioned so that it has a lower spring force than the spring member 199, so that the control arm 185 and the extendable guide 183 as a unit relative to the holder 186 from the fully retracted position of the control arm (before the control arm 185 engages the Cord guide arm 34) can be moved into a second extended position against the action of the spring arrangement 191 depending on the engagement of the cord guide arm 34 on the control arm 185. In the second control arm position the knife 177 rests on the abutment 175. According to a feature of the invention, the cord guide arm 34 can then be moved further to further extend the control arm 185 from the second position to a third position. During this movement of the control arm 185 from the second to the third position, the expandable guide 183 is stationary and the movement of the control arm 185 is made possible in that it is movable relative to the expandable guide 183 by compressing the spring member 199 between the washer 203 and the stop plate 201 . Driving over the line guide arm 34 to move the control arm 185 from the second to the third position is desirable, so that an adjustment can be made to compensate for the wear of the components of the line separating device 35 and this does not require a great deal of time. For example, the knife edge may have become blunt or other components may have worn out or become loose. Nevertheless, the knife 171 can reliably engage the abutment 175 since the line guide arm 34, with its movement going beyond, enables a longer stroke of the control arm 135, which is required for the knife 177 to engage the abutment 175. Also, with the possibility of the line guide arm passing over the end position, the initial adjustment and the compensation of the manufacturing tolerances are less difficult, so that larger tolerances can be permitted. It is also no longer necessary to carefully monitor the end of the movement of the line guide arm so that the end coincides exactly with the initial touching of the knife 177 and the abutment 175 in order to avoid excessive stress or bending of the knife edge on the abutment.

When the cord separator 35 is in its inactive position, the knife 177 is rotated to a substantially horizontal position, as shown in FIG. 13 shows, is determined by the spring arrangement 191 on the control arm 185 and by the pull-out guide 183. Due to the design, a slight pre-compression is provided in the spring member 199 due to its displacement between the stop disc 203 and the stop 201. In the inactive position, a slight bias is also maintained in the spring assembly 191 to keep the components in mutual tension. When the line guide arm 34 is moved from the second position near the side wall 17 to the home position near the side wall 18, the line guide arm engages the control arm 185 to initially move it from the non-extended position to a second extended position against the bias of the spring assembly 191 to move until the knife 177 comes into contact with the abutment 175. During the movement of the control arm from the first to the second position, the extendable guide 183 and the control arm 185 move as an integral unit. The length of the movement from the first to the second position is approximately 4 cm for the control arm 185, for example. The cord guide arm 34 then continues to move to further extend the control arm 185 from the second to the third position and against the bias of the spring member 199. This spring element is compressed and allows the control arm 185 to be relatively movable with respect to the guide 183 now defined. The length of the path from the second to the third position of the control arm can be, for example, approximately 6 mm. The cord 33 is severed when the knife 177 initially engages on the abutment 175, ie when the control arm 185 reaches its second position. The cord separator 35 is held in this actuation position until a further cord binding process is triggered by sensing a finished bale in the wrapping chamber. When a bale is finished, the control device 29 activates the hydraulic drive 32 to move the line guide arm 34 from the first position near the side wall 18 into the second position near the wall 17 to move. The opposite movement of the cord guide arm 34 allows _d ate the spring arrangements 191 and 199 the extension guide 183 lead back to the retracted position, the control arm 185 to its first position and blade 177 to take the lifted from the abutment position. The cutting device is held in the inactive position until the line guide arm 34 has been returned to the first position near the side wall 18 by reversing the hydraulic drive 32.

The hydraulic drive device is described in more detail below with reference to FIG.

The binding device 12 is shown schematically in FIG. For this purpose, a circuit diagram for the reversible hydraulic drive 32 of the reciprocally movable cord guide arms 34, 36 of both embodiments is shown. The hydraulic actuator 32 comprises a double-acting hydraulic cylinder 112, a hydraulic pump 38 which is connected to the cylinder 112 via a four-way two-position slide valve 39. A control valve 211 used to adjust the flow has a bypass line 213, both of which are provided in line 215, which connects an opening of the valve 39 to the base opening 217 of the hydraulic cylinder. The action of the control valve 211 controls the fluid flow to the left and the fluid flow to the right passes through the bypass line 213 and is thus uncontrolled. The fluid flow that serves to extend the piston 108 of the hydraulic cylinder 112 is thus uncontrolled, while the flow for retracting the piston is controlled. A liquid supply 219 is connected to the valve 39 via a filter 221.

In operation, Fig. 11 shows the state of the hydraulic drive between two bale wrapping cycles. This means that the state is shown in which the wrapping chamber 22 is empty or a bale is still formed in the chamber. Between the binding processes, the actuating arm 89 is in the position A according to FIG. 3. In this position, the pump 38 is not driven by the drive 37, so that no fluid can get into the front opening 223 of the cylinder from the pump 38. When a bale is fully formed, the control device 29 triggers a displacement of the actuating arm 89 from the A position to the B position. This activates the pump drive 37 for the pump 38. When the valve operating arm 89 is moved from position A to position B, the slide of the valve is pushed outwards. As a result, the fluid path between the pump 38 and the base opening 217 is established via the bypass line 213 of the control valve 211. After activation of the pump drive 38, the piston 108 of the cylinder 112 is extended and the fluid flows from the front opening 223 through the valve 87, the filter 221 into the reservoir 219. When the actuating arm 89 is moved from the B position to the C position , the spool of valve 39 moves inward to create a flow path between pump 38 and front opening 223 so that piston 108 of cylinder 112 is retracted. During the withdrawal, the fluid is directed from the base opening 212 through the adjustable flow control valve 211, which controls the flow rate. From the valve 211, the fluid passes through the valve 39, filter 221 into the container 219. The cord 33 is severed by the separating device 35 when the piston 108 is fully retracted. The binding of the bale has now been completed and the bale is ejected by the operator. After ejection, the control device 29 will switch off the pump drive 37 and switch the actuating arm 89 from position C to position A. If the Control arm 89 is moved back from position C to position A, the position of the slide of the valve 87 remains unchanged. The hydraulic drive 32 is thus switched off until a new binding process is triggered.

Claims (31)

1. Automatic binding device for machines for the production of cylindrical bales from harvested material in a winding chamber, with a cord dispenser for inserting a cord into the winding chamber for wrapping the cylindrical bales, which has a cord guide arm which moves back and forth between end positions in an area in front of the wrapping chamber is movable here, and with a hydraulic drive for cyclical reciprocation of the line guide arm, which has a double-acting cylinder, a feed pump, a pump drive for selectively driving the pump and a control valve between the pump and cylinder, with a valve actuating arm between a first position , in which the cord guide arm is movable from a first to a second position and is movable in a second position in which the cord guide arm is returned to the first position, characterized in that a control device (29) for triggering a binding process by h automatic switching on of the pump drive (37) and for moving the valve actuating arm (89) is provided in its first position, which responds to the formation of the cylindrical bale (24) and to reaching a predetermined bale diameter, and that the control device (29) Pump drive (37) switches off automatically when the binding process is finished. 2. Binding device according to claim 1, characterized in that the control device (29) a depending on the increase in bale diameter from a first position, which corresponds to the empty wrapping chamber (22) or a bale of insufficient diameter, in a second position Bell lever (41), which second position is assigned to a bale diameter corresponding to or exceeding the predetermined value, which bell lever triggers the actuation of the pump drive (37). 3. Binding device according to claim 2, characterized in that the pump drive (37) consists of a belt drive with a driving and a driven pulley (71, 73) and a tensioning device (65) which in and out of engagement with the associated belt (75 ) is movable, and that the control device (29) has a linkage for actuating the tensioning device (65) and a tensioning spring (53) which is arranged between the bell lever (41) and the linkage and the tensioning device (65) as a function of the Moves the bell lever in its second position in the engaged position. 4. Binding device according to claim 3, characterized in that the control device (29) has a locking device (77) for locking the linkage in the disengaged position, and a trigger element (79) is provided, which with the bell lever (41) for opening the locking device is connected when the predetermined bale diameter is reached. 5. Binding device according to claims 3 or 4, characterized in that the control device (29) resets one on the bell lever (41) acting spring arrangement (53,84,91,93) and a return spring (86) returning and holding the locking device (77) into the blocking position. 6. Binding device according to one of claims 2 to 4, characterized in that the control device (29) between a valve actuating arm (89) and the bell lever (41) has a spring (91) for biasing the actuating arm (89) into its first position when triggered of the binding process and depending on the movement of the bell lever (41) to the increase in the bale diameter. 7. Binding device according to claim 6, characterized in that the biasing spring (91) of the actuating arm (89) from the control valve (39) biases the actuating arm from its first position in the direction of the second position and the actuating arm against movement into the second position blocking locking device (95) is provided, the locking device having an actuating arm (101) which, by means of the cord guide arm (34) when it moves from the first to the second position, for releasing the locking device and releasing the actuating arm (89) for movement into it second position is adjustable. 8. Binding device according to claim 7, characterized in that the control device (29) has a return spring (93) which biases the actuating arm (89) for the control valve (39) from the second towards its first position when the bell lever (41) is in its first position. 9. Bindeeinricntung according to claim 8, characterized in that the return spring (93) is designed and arranged so that it also biases the actuating arm (89) in a third position, and that the control device (29) is designed so that the Actuating arm (89) can be automatically moved from the third to the first position by the biasing spring (91) when a binding process is triggered. 10. Binding device according to claim 9, characterized in that the control valve (39) is a two-position valve and is in the same position when the actuating arm is in its second and its third position. 11. Binding device according to one of claims 1 to 4, or claim 9, characterized in that the control valve (39) is a two-position slide with a pin attached to the slide (92) on which a lever member (94) of the actuating arm (89) is pivotable is articulated so that when the actuating arm is moved from the third to its first position in a first direction and when it is moved from the second to the third position in the opposite direction about the articulation point, and that the control valve (39) in the same position is when its actuating arm (89) is in the second or third position. 12. Binding device according to one of claims 1 to 11, characterized in that the valve actuating arm (89) can be automatically transferred into its third position by the control device (29) when the hydraulic drive is switched off at the end of a binding process. 13. Binding device with a in front of a winding chamber for cylindrical bales by means of a reversible drive reciprocable cord guide arm, characterized in that the drive (32) has a pinion (127) for pivoting the cord guide arm (36) back and forth between its end positions and a coupling device (141) is assigned to the pinion, such that the cord guide arm (36) can remain in the region of an end position. 14. Binding device according to claim 13, characterized in that the toothed drive (127) has a first toothed member (129) in driving connection with the cord guide arm (36), which has a toothing (33) over a partial circumference, and a second toothed member (143 ) in drive connection with the drive (32), which has a peripheral region with teeth (135) for direct engagement in the teeth of the other tooth member, and that the coupling device (141) on one of the tooth members a peripheral surface portion (143) to interrupt the Has engagement and for further driving the second toothed member (134) without driving the first toothed member (129) connected to the cord guide arm (36). 15. Binding device according to claim 14, characterized in that the peripheral surface section (143) of the coupling device (141) is a tooth-free section of one of the tooth members. 16. Binding device according to claim 14 or 15, characterized by a biasing device (147) for biasing the first, with the cord guide arm (36) connected tooth member (129) in the direction of direct engagement with the other tooth member (134) after the drive has been interrupted. 17. Binding device according to claim 16, characterized in that the biasing device (147) has a lever (149) on the first tooth member (129) and a spring device (151) on which the lever (149) during the movement of the line guide arm (36) in the direction of an end position before actuating the coupling device (141), in order to store spring energy in the spring device, which is buried when the drive (32) is reversed for returning the line guide arm (36). 18. Binding device with a cord separating device, consisting of a cutting abutment, a knife and an actuating device which, depending on the movement of a cord guide arm which can be moved back and forth in front of a winding chamber for cylindrical bales, into a predetermined position near one of its end positions between a first and a second position movable control arm which moves the knife from the abutment to a position cooperating with the abutment, characterized in that the actuating device (181) has an extendable guide device (183) which with the control arm (185) and with the Knife (177) is connected such that the control arm (185) can be moved from its second position into a third position depending on the further movement of the line guide arm (34, 36) beyond the predetermined position, and that the actuating device (181) the knife in its position the abutment holds as long as the control arm is moved to the third position and is in this third position. 19. Binding device according to claim 18, characterized in that in the region of the sides of the winding chamber (22) a holding device (186) for supporting a pretensioning device (191) seen, which biases the control arm (185) towards its first position, that the guide device (183) has a biasing element (199) of greater biasing force than that of the biasing device, which biases the control arm (185) in a retracted position, that the control arm (185) and the guide device (183) as a unit are movable relative to the holding device (186) and against the pretensioning of the pretensioning device (191) when the control arm (185) moves from its first to its second position, that the guide device (183) is connected at one end to the knife (177) and at the other end to the control arm (185) that the movement of the guide device (183) is stopped when the knife (177) engages the abutment (175) and that the guide device (183) and the knife (177) remain at a standstill when the control arm (185) relative to this unit from the second position to the third position against the force of the Preload element (199) is moved. 20. Binding device according to claim 19, characterized in that the knife (177) is pivotally mounted (179) and is designed as an angle or bell lever, at one end of which the guide device (183) is articulated, which in turn has two slotted slots at its other end Arm regions (189, 197), while the control arm (145) has a pin sliding in the slots and the biasing member (199) biases the control arm (185) to the retracted position where the pin rests against one end of the slots. 21. Binding device according to claim 20, characterized in that the control arm (185) is rod-shaped and the pretension direction (191) is a spring threaded onto the rod between the holding device (186) and the slotted arms (189, 197), the slotted arms forming a stop, through which the rod-shaped control arm extends and between the slotted arms and between the stop and the biasing member (199) carries the pin sliding in the slots. 22. Binding device according to claim 21, characterized in that the control arm (145) has at one end a contact section for the line guide arm (34, 36) and the actuating device (181) is movable in dependence on the engagement of the line guide arm on the contact section. 23. A binding device with a line guide member which can be moved back and forth in front of a winding chamber for cylindrical bales, characterized in that the line guide arm (34, 36) pivotally supported at one end has an elongated, freely accessible line guide surface (116) and a tubular line guide at the free end (107, 123), the length of which is considerably less than that of the line guide surface (116). 24. Binding device according to claim 23, characterized in that the cord guide surface (116) is provided on an elongated U-shaped support part (109). 25. Binding device according to claim 23 or 24, characterized in that a tensioning device (114) holding the cord (33) on the surface (116) is provided in the region of the cord guide surface (116). 26. Binding device according to claim 25, characterized in that the cord tensioning device (114) a tensioning plate (118), a mounting device (122) with a biasing element (126) for holding and biasing the tensioning plate (118) against the guide surface (116) and in mutual Has spacing and guide pins (128, 130) arranged at the entrance (136) or at the exit (138) of the cord tensioning device (114), a cord guide path being delimited between the pins on one side and the mounting device (122) on the other side. 27. Binding device according to claim 26, characterized in that the mounting device (122) has a bolt (124) and a spring (126) threaded thereon. 28. Binding device according to claim 26 or 27, characterized in that on the input side the leading edge of the plate (118) is chamfered away from the line guide surface (116) and the plate (118) has a third side (142) which is located between the input (136 ) and exit (138) and has a beveled edge (140) away from the guide surface. 29. Cord tensioning device, characterized in that a cord guide surface (116) and a tensioning plate (118) are provided, which tensioning plate can be fastened to the guide surface by means of a mounting device (122) and can be urged against the guide surface (116) by means of a spring biasing device (126) and that two guide pins (128, 130) are arranged near and opposite the entrance (136) and the exit (138), the pins on one side and the mounting device on the other side providing a guide path for the cord (33) form. 30. Cord tensioning device according to claim 29, characterized in that the mounting device (122) has a bolt (124) and a spring (126) threaded thereon. 31. A cord tensioning device according to claim 29 or 30, characterized in that on the input side the leading edge of the plate (118) is chamfered away from the cord guide surface (116) and the plate (118) has a third side (142) which is located between the input (136 ) and outlet (138) and has an edge (140) which is also bevelled away from the guide surface (116).

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